Glassware forming machine



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GLASSWARE FORMING MACHINE Filed Deo. 2l, 1931 -ll Sheets-Sheet 5 1l Sheets-Sheet 6 Nov. 27, 1934.

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s y \\\\\\\\\\\\\\\\\f//// Nov. 27, 1934. R. G. ALLEN ET AL GLASSWARE FORMING MACHINE Filed Deo. 21, 1951 11 Sheets-sheet 11 Patented Nov. 27, 1934 UNITED STATES PATENT OFFICE 1,981,937 GLASSWARE FORMING MACHINE a corporation of Ohio Application December 21, 1931, Serial No. 582,346

49 Claims.

The present invention relates to improvements in glassware forming machines and more particularly to machines of the well-known Owens type, such, for example, as that shown in the La France Patent 1,185,687, dated June 6, 1916, to which reference may be had for details not disclosed in or forming part of the present application. Machines of this type include an annular series of mold groups or heads which rotate continuously about a vertical axis andare thereby brought in succession to a series of operating positions. In one of these positions the mold groups gather mold charges of molten glass and in the succeeding positions these mold charges are subjected to different operations and thereby transformed into finished articles of glassware. Each mold group or head, includes a blank forming unit and a finishing mold, the former consisting of partible cooperating body blank and neck molds, a cut-off knife, a plunger, and means for alternately raising and lowering the entire unit as well vas` -vacuum and air pressure regulating devices.

Ordinarily, and in accordance with the present invention, opening and closing of the body blank and neck molds as well as actuation of the cut-off knife, and raising and lowering of the plunger, as well as the entire blank forming unit, are controlled and regulated by cams supported on a stationary central column about which the mold carriage rotates. Where these cams or portions thereof `are incapable of being adjusted to -advance or retard the position of one or more operations with respect to others, it is practically impossible to obtain and/or main-tain a proper standard of quality in the articles of glassware being produced. This is to a considerable extent true even where articles of a given size and shape are produced over a comparatively long period of time. and is particularly true where frequent mold changes are made for the purpose of manufacturing articles of different shapes, sizes, and/or weights. In the first instance, varying conditions in the glass batch -as well as atmospherc conditions, may and frequently do require advancing or retarding of the dipping of the molds into the supply body of glass, retraction of the plunger, and/or opening of the body blank and neckmolds. changed, for example. to produce articles varying in shape and/or weight as compared with a preceding operation, changing the relative positions of and in many instances, the duration of the various operations is absolutely essential to the production of marketable glassware. For ex- In the event the molds are' ample, if the molds are changed to produce a comparatively large heavy article of glassware, it is quite probable that the duration of contact Ibetween the blank mold and glass must be lengthcned in order to insure complete filling of the body blank and neck mold cavities. Also, it probably will -be necessary to retard dropping of the knife out of contact with the mold bottom so that the compacting or blowdown operation which tends to solidify the blank and fully form it, may be prolonged. Also, the period of contact between the plunger and glass will be extended further than with the smaller articles so that the glass forming the neck portion will be completely set prior to the compacting blow. This is necessary to prevent the compacting blow from blowing the glass out of the neck mold. Opening of the body blank mold will necessarily Ibe delayed for the purpose of insuring the formation of a film or enamel of sufficient thickness to prevent distortion of theY blank. In many instances it will be found during operation of the machine that one or more of these operations should be adjusted relative to the others in order that glassware of a high standard of quality may be consistently produced.

An outstanding feature of the present invention is the provision of novel means whereby the various operations may be adjusted as and for the purpose indicated above.

Another object is the provision of improved means for independently adjusting the cam.

mechanisms which control the various operations without interrupting normal operation of the machine.

A further object is the provision of novel means for adjusting the various cam mechanisms one at a time, this means consisting of a. single control lever having two operating positions and serving to select the cam mechanisms to be adjusted as well as to adjust the selected mechanism.

It is also an object of the present invention to provide automatic means for securing the cam mechanisms against accidental'movement after .an adjustment has been effected.

Another object is the provision of automatic means for indicating the limits of adjustment of the cam mechanisms so that overlapping of certain operations with obvious disastrous results may be avoided.

A further object is the provision of novel cam construction in which an adjustable angular portion is formed with a flexible extension adapted at times to form part of one wall of the cam.

Other objects will be in part apparent and in part pointed out hereinafter.

In the drawings:

Fig. 1 is a vertical sectional view with parts in elevation, showing our invention embodied in an Owens type bottle machine.

Fig. 2 is a cam chart on which the relative positions of the various operations are indicated.

Fig. 3 is a detail sectional plan view through the entire central column of the machine, taken substantially along the plane of line III-III of Fig. 1.

Fig. 4 is a view similar to Fig. 3 taken along the plane of line IV-IV of Fig. 1.

Fig. 5 is a detail top plan view of the control box for the cam selecting and adjusting devices.

Fig. 6 is a vertical sectional view with parts in elevation taken substantially along the line VI-VI of Fig. 5.

Fig. 7 is a sectional view of the clutch mechanism taken substantially along the line VII- VII of Fig. 6.

Fig. 8 is a longitudinal sectional view of the clutch.

Fig. 9 is a detail view showing the separable connection between the operating handle and the adjusting means.

Fig. 10 is a fragmentary top plan view showing the dip cams which control the vertical movements of the blank molds at the charging position.

Fig. 11 is a sectional view taken along the line )Ui- XI of Fig. l0 showing the cam for lowering the blank molds.

Fig. 12 is a view taken along the line XII- XII of Fig. 10 showing the cam for raising the blank molds after the charging operation.

Fig. 13 is a fragmentary plan view showing the chain extension which constitutes part of the outer wall of the lifting cam when said cam and the lowering cam are spaced apart.

Fig. 13-A is a plan view showing the two clip cams.

Fig. 14 is a fragmentary bottom plan view of the cam for controlling opening of the neck molds.

Fig. 14-A is a detail fragmentary plan view of the adjustable angular portion of the cam.

Fig. 15 is a sectional view taken substantially along the line XV-XV of Fig. 14.

Fig. 16 is a sectional view taken along the line XVI--XVI of Fig. 14. l

Fig. 17 is a fragmentary bottom plan view showing the cam for lifting the plungers.

Fig. 18 is a sectional view taken along the line XVIII-XVIII of Fig. 17.

Fig. 19 is a fragmentary sectional plan view of the blank mold opening cam taken along the plane of line XIX-XIX of Fig. 1.

Fig. 20 is a sectional view taken along the line XX--XX of Fig. 19.

Fig. 21 is a sectional view taken along the line XXI- XXI of Fig. 19.

Fig. 21-A is a plan view showing the adjustable cam sections.

Fig. 22 is a fragmentary top plan View showing the cams for swinging and lowering the cut-off knives.

Fig. 23 is a transverse sectional view taken along the line XXIII- XXIII of Fig. 22.

Fig. 24 is a transverse sectional view taken along the line XXIV-XXIV of Fig. 22.

Fig. 25 is a sectional elevational View of another form of means for selecting and adjusting the individual cam mechanisms including a Cam location indicator.

Fig. 26 is a sectional view taken along the line XXVI- XXVI of Fig. 25.

Fig. 27 is a detail perspective View of the operating handle and indicator.

Fig. 28 is a sectional elevational view of another form of means for selecting and adjusting -the individual cam mechanisms.

Fig. 29 is a fragmentary plan view illustrating automatic means for securing the cams against accidental movement.

In more or less general terms the present invention which, as indicated above, may well be embodied in an Owens suction type machine, includes selecting and adjusting devices disposed for the greater fpart within the usual stationary central column. These selecting and adjusting devices have direct and individual connection to the cams so that they may be adjusted one at a time about the central column. A manually operable crank lever is employed to actuate the cam selecting and adjusting devices, said crank lever having two operating positions, in one of which itis operable to select the cam to be adjusted, while in its other position, operation thereof adjusts the selected cam. All of these selecting and adjusting operations may be easily effected without interrupting the normal operation of the machine.

In the present invention the adjustable cams are those controlling the operations involved in gathering mold charges from a supply body of molten glass and transforming them into blanks or parisons which are later enclosed in finishing molds and expanded to the final shape of the articles being produced.

In the machine with which one embodiment of our invention is shown, the construction includes a wheeled base 40 supporting a stationary central column 41 upon which the mold carriage 42 is mounted for continuous rotation. Rotation of the mold carriage may be obtained by any conventional or preferred means, such, for example, as a variable speed electric motor (not shown) operatively connected to a ring gear 43 at the lower end of said mold carriage. This mold carriage supports an annular series of mold groups 44 each of which includes a blank or parison forming unit 45 and a finishing mold unit 39. These mold groups are identical in construction and operation, each in effect constituting a complete bottle forming unit.

Each blank or parison forming unit is of conventional form and includes cooperating partible body blank and neck molds 46 and 47 respectively, which are connected to a vertical hinge pin 48 carried by a forward extension 49 at the lower end of the dipping frame 50. A plunger 51 arranged above the blank and neck molds is adapted to cooperate with said molds at regular time intervals in forming the neck and finish or sealing surface, of articles being produced on the machine. A cut-off knife 52 is supported in the usual manner and adapted to be swung across the lower end of the corresponding blank mold at regular time intervals to sever gathered mold charges j' from the supply body of glass. Later this knife is lowered away from said mold preparatory to swinging it to an inoperative position. Opening and closing of the blank and neck molds as well as raising and lowering thereof and operation of nected at one end to the dipping frame 50 and A at its other end to a rod 54. This rod is pivoted to a slide carrying a roller 56 which runs in and is moved radially of the mold carriage by a dip cam 57. The cam 57 (Figs. 1, 10 to 13A inclusive) is secured to the central column 4l and includes two adjustable sections one of which lowers the mold into the glass. The other cam section raises the mold out of contact with the glass.

Both sections of the dip cam are slidingly supported in guideways 58 provided on the upper side of a stationary cam plate 59 or table which is attached to the central column 41. One cam section 60 (Figs. 10, 11, 13, and 13A) constitutes the angular portion of the cam 57 which controls lowering of the molds into contact with the glass. This cam section is adjustable as stated above for the purpose of advancing or retarding the point of initial contact between the molds and molten glass. The construction whereby such adjustment may be accomplished includes a segmental rack bar 61 secured to the inner margin of the cam section 60. This rack bar is disposed in the inner guideway 58 and runs in mesh with a gear62 which in turn is operatively connected to a worm 63 at the outer end of a control shaft 64. The gear 62, worm 63, andshaft 64, are journaled in suitable bearings on the cam plate 59. By rotating the shaft 64 through the use of' mechanism to be described hereinafter, the operating position of the angular cam section 60 may be changed as conditions may require.

The other angular cam section 65 which controls and regulates the point. at which the molds are lifted away from the supply body of molten glass includes an angular portion 6 6 which causes the cam roll 56 on each dipping unit to move radially outward and thereby raise said unit. Adjustment of this cam section 65 circumferentially relative to the other section 60 is obtained through the provision of a segmental rack bar 67 at the inner margin thereof. A gear 68 is operatively connected to the rack bar and meshes with a worm 69 at the outer end of a control shaft 70, said gear, worm, and shaft, being journaled in suitable bearings on the stationary cam plate 59 or table. In order to avoid the creation of a gap in the outer cam wall when the two sections are adjusted away from each other, the section 65 which raises'the molds, is provided at one end with a flexible extension 71 (Figs. 10, 13, and 13A) This extension may be in the form of a chain secured to one end of the outer Wall of the cam 65 and normally lying within a channel 72 provided in the other adjustable cam section 60. Thus it will be Vseen that when the two angular sections 60 and 65 are adjusted away from each other the chain extension will automatically move into position to ll in the space between said sections and thereby form a portion of the outer wall-of the cam. The gap between the adjacent ends of the inner walls of the cam sections is compensated for through the presence of the strip 4forming the inner guideway 58. With a construction such as that just set forth it is apparent that the duration of .19 to 21-A inclusive).

.inner vertical wall of the adjacent contact between the molds and the supply body of glass as well as the point of raising and lowering the molds may be adjusted at will and, as will be apparent hereinafter, without interrupting normal operation of the machine.

The blank and neck molds which are pivoted to the hinge pin 48 are adapted to be opened and closed in the usual well-known manner, involving first, the opening of vthe blank mold, and then, after the blank or parison has been enclosed in a finishing mold, an additional opening movement on the part of the blank mold to thereby open the neck mold. Links '73 (Fig. 1) connect the mold arms to a slide 74 which is suitably connected to a second slide 75 carrying a cam roll 76 running in a cam 77 (Figs. 1, 14 to 16, and This cam 77 is arranged on the lower side of the stationary cam plate 59 which carries the dip cams 60 and 65 and includes` a blank mold opening section 78 (Fig. 19) and a neck mold opening section 79 (Fig. 14). These cam sections are individually adjustable so that the points of opening the blank and neck molds may be advanced or retarded to meet the particular requirements of the glassware being produced. As pointed out heretofore, in the pro- Aduction of comparatively large articles of glassware, it is necessary to retain the blank molds in contact with the gathered glass for a greater length of time than in the production of comparatively small articles of glassware, this being so because a heavier enamel or film of chilled glass is reduired to hold a large blank against distortion than a small blank. vThe blank mold opening cam 78 (Figs. 19 to 21 inclusive) consists of an angular portion 80 arranged between and secured to end sections 81 and 82. This cam '78 is slidingly supported in guideways 83 which include marginal strips 83a separably attached to ribs 84 on the stationary cam plate 59. A flange 85 at the inner margin of the angular cam portion 80 has sliding contact with the lower surface of the inner rib 84. This angular cam portion is also formed with a longitudinal groove86 adapted at times to receive a tongue 87 provided on the rib 84. This tongue and groove construction assists in supporting the adjustable cam. For the purpose of adjusting the cam section 78, we have provided a construction including a segmental rack bar 88 along one wall of a vertical opening 89 in the end section'82 and a gear 90 extending into said vertical opening and meshing with the rack bar 88. This gear 90 is secured to one end of a vertical shaft 91 which is journaled in a bearing formed in the cam plate 59 and carries at its other end a worm gear 92 meshing with a Worm 93. This worm is secured to the outer end of a shaft 94 which is journaled in bearings on the cam plate 59, and adapted to be operated by mechanism to be described in detail presently. Through rotation of the gear 90 (Figs. 19 and 21) the cam 78 may be adjusted circumferentially of the machine to locate the angular portion 80 at any point between the full positions indicated in Fig. 19. l

The neck mold cam section 79 (Figs. 14, 14-A, 15. and 16) which is located approximately 270 dot and dash line A degrees from the charging position (Fig. 2) and I mold cam, constitutes A well known conventional construction and operation such, for example, as that set out in the La France patent above identied.

This neck mold cam 79 operates to move the cam roll 76 (Fig. 1) radially inward a short distance beyond the point necessary to initially open the blank mold, with the result that the corresponding neck mold is opened sufficiently to free the neck of the article which at this point in each cycle of operation is about to be lowered in and with the finishing mold 39 preparatory to passing beneath the revolving pot (not shown). Such movement of the cam roll 76 is due to its engagement with the angular portion (Figs. 14 and 14--A) provided at the inner margin of the movable cam. By adjusting this angular portion 95 and providing a temporary cam wall to fill in the gap created by the movement of this angular portion, the point at which the cam roll 76 is initially moved radially inward, as well as the duration of the period of travel in such radial position, may be regulated and controlled. The specific construction for accomplishing the above may be substantially as follows. The inner wall 96 is stationary and offset inwardly between points A and B (Fig. 14) to permit inward movement of the cam roll under the influence of the angular portion 95 of the adjustable cam section. The outer wall 97 is stationary and disposed concentric to the inner wall and terminates at the line C (Fig. 14). The adjustable cam section includes the angular portion 95 provided at the inner margin of the plate 98 and a chain extension 99 which is arranged in a channel 100 or groove provided in the cam plate 59 and covered by a plate 101. This chain extension 99 is adapted to fill in the space between the angular portion 95 and the outer cam wall to the left of said angular portion in Fig. 14, when the latter is adjusted to the right to retard the point at which the neck mold is opened and lengthen .the period of time during which said mold is held closed. When the cam is adjusted to the right in Fig. 14, the chain extension 99 moves in the guideway 102 provided by the rail 103 and the outer cam wall 97 with the result that said extension in effect forms a continuation of said angular portion 95. For the purpose of adjusting this angular portion, a segmental rack bar 104 is attached thereto and runs in mesh with a gear 105 which is mounted on a. vertical shaft 106. This shaft also carries a worm gear 107 having operative connection with a worm 108 at the inner end of a control shaft 109. This shaft, as are the other control shafts, is operated by means which will be described presently.

, An adjustabe plunger lifting cam 110 is mounted upon a stationary cam plate 111 which is secured to the central column 41, said cam regulating and controlling the lifting of the plunger 51 out of and away from the blank and neck molds after the mold charging operation. A stationary cam 112 on the plate 111 (Fig. 17) is arranged for cooperation with the adjustable cam 110 and may well be of conventional form. This adjustable cam 110 is slidingly connected to the stationary cam plate 111 by means of outer and inner retaining strips 113 and 114 respectively, which take over opposed marginal portions of the cam and form guideways therefor. At the inner margin of the cam opposite the angular portion 115, a segmental rack bar 116 is attached thereto and runs in mesh with a gear 117 which is journaled upon a shaft 118, said gear having operative connection to a worm 119 at the outer end of a shaft 120. This shaft 120 extends into the central column 41 for operative connection to adjusting means which will be described later.

On the upper side of the cam plate 111, which carries the vplunger lifting cam, we have provided an adjustable cam 121 (see Figs. 22 and 24) for swinging the cut-,01T knife 52 across the lower end of the corresponding blank mold, and an adjustable cam 122, the function of which is to lower the cut-off knife out of contact with the bottom of the mold after the charge severing operation and the usual compacting blow preparatory to returning said knife to its inoperative position. The adjustable knife swinging cam 121 (Fig. 22) forms a continuation of the stationary cam 123 in which the cam roll 124 carried by the knife swinging mechanism is guided. This cam 121 includes an angular portion 125 arranged to move the roller 124 radially outward at the time it is desired to swing the cut-off knife across the lower end of the corresponding blank mold. In order that the point' of swinging the knife may be changed to meet the varying operating conditions, such for example, as a change in the point of lift of the blank mold, this cam, with the angular portion 125, is slidingly supported on the stationary cam plate 111. A segmental rack bar 126 is attached to the cam 121 and runs in mesh with a gear 127 secured to one end of a vertical shaft 128. A worm gear 129 at the other end of the shaft 128 meshes with a worm 130 at the outer end of a shaft 131 which extends into the stationary central column 41 for connection to selecting and adjusting means which will be described presently.

The cam 122 which is adjustable to change the point at which the knife 52 is lowered away from the corresponding blank mold following the charge severing operation, is arranged inwardly and circumferentially from the knife swinging cam 121 and includes a segmental rack bar 138 at its inner margin meshing with a gear 132 operatively connected to a gear 133 which in turn is rotatable by adjusting means to be described. The first gear 132 projects through an opening in the wall of the central column 41 for engagement with the rack bar 138. The outer wall 134a of the stationary portion 134 of the knife drop cam is shaped to move the cam roll 135 of the knife lowering mechanism radially inward a short distance in advance of the swinging movement of the knife. Thus the knife is brought to such an elevation that when it swings across the lower end of the mold it will effectively seal the mold cavity or cavities, said knife being held in this elevated position by the stationary outer wall 134. The wall 136 of the adjustable cam cooperates with a portion of the outer wall 134a in providing `a substantially continuous bearing surface for contact with the cam roll 135. The cam 122 operates to positively. move the cam roll 135 radially outward at a predetermined variable point beyond the knife swinging position to thereby insure lowering of the knife away from the mold prior to swinging it to an inoperative position.

Each of the finishing mold units 39 (Fig. 1) is of conventional form and includes a carrier 39a pivoted to the mold carriage 42 and adapted to be alternately raised and lowered on the serpentine track 39h. A cam 39c operates through suitable mechanism to open and close the mold at regular time intervals.

In order that the adjustable cams described above may be placed in various positions to thereby change the timed relation between and duraand in part resting upon tion of the successive operations on gathered mold charges of glass, a selecting device and an adjusting device common to all of the molds are arranged within the lower portion of the central column 41. These devices may be operated to respectively select and adjust the cams without interfering with normal operation of the machine. Through the medium of a single operating crank lever, the selecting device is caused to provide connection between the desired cam and the adjusting device, said lever then being operable to adjust the selected cam as may be required by the particular operating conditions.

These selecting and adjusting devices (Figs. l, and 5 to 9, inclusive) are for the greater part arranged within a stationary drum-like casing 140 which is supported in the lower end of the central column 41. Arms 141 on said casing are bolted or otherwise secured to said column. An integrally formed bottom 142 closes the lower end of the casing while a removable cover plate 143 closes the upper end thereof. A rotary adjusting shaft 144 extends vertically and centrally through the casing 140. The upper end portion of the shaft 144 is journaled in a bearing 145 and held against axial movement therein by avcap 146 which is secured to the upper end of the shaft and rests upon the bearing 145. The lower end of this shaft 144 is journaled in a bearing 147 provided in a bracket 148 which is attached to the lower side of the casing 140. A gear 149 secured to the shaft 144 within the casing 140 and immediately below the upper bearing 145, constantly meshes with an annular series of pinions 150, individual to the shafts and cams. A bevel gear 151 is connected to the shaft 144 just above the lower bearing 147 and meshes with a bevel pinion 152 which is adapted to be rotated at times for the purpose of imparting rotary movement in either direction to the shaft 144 and gear 149 secured thereto, and therebyadjust the position of a cam. The direction of rotation is dependent upon the direction in which the selected cam is tov be adjusted.

Although all of the pinions 150 rotate together with rotation of the main gear 149, the construction is such that only one pinion at a time is operatively connected to a cam. The construction whereby this operating condition is obtained, may be as follows. A clutch 159a is arranged to provide separable driving connection between each pinion 150 and the corresponding shaft which extends upwardly to one of the horizontal shafts having connection with an adjustable cam. Each pinion 150 constitutes a part of one of the clutch mechanisms and is loosely mounted upon a vertical pin 153, which extends a considerable distance above and below the pinion and has its lower end extending through and termnating a short distance below a bearing sleeve 154 carried by a holder 155. This bearing sleeve may be releasably secured in the holder by a set screw 156. An upstanding annular flange `157 formed on the upper end of the bearing sleeve 154 the upper end of the holder 155 is provided with diametrically opposed notches 158 in which the opposed ends of a clutch pin 159 carried by the vertical pin 153 are adapted to seat. A depending flange 160 on the lower side of the pinion 150 is provided with diametrically opposed notches 161 which are adapted at times to receive the ends of the clutch pin 159 and thereby provide positive driving connection between the vertical pin 153 and the corresponding pinion 150. Such positioning ofthe clutch pin to effect driving connection between the pinion and vertical pin is obtained by mechanism to be described presently. The upper end of the vertical pin 153 has splined connection to the lower endl of one of the vertical shafts which lead upwardly from the selecting and adjusting devices to the cams. A coil springp153a extends into an upwardly facingV opening in the pin 153 and has itsupper end bearing against the sleeve 163. This spring yieldingly holds the pin 153 in its lowermost position. A coil spring 162 (Fig. 6) encircles a sleeve 163 into which the vertical pin extends and an upward sleeve extension 164 on the pinion, said spring operating to yieldingly hold the pinion in its lowermost position whereby the notched flanges 157 and 160 are held in contact with each other at times. An antifriction device 165 is disposed between the lower end of the coil spring 162 and the pinion so that the latter may rotate freely.

For the purpose of operatively positioning the clutches 159a one at a time so that any one cam may be adjusted, manually controlled mechanism including the following construction is employed. A selector arm 170 is mounted for movement about the axis of the vertical shaft 144 (Fig. 6) said arm being provided at its outer end with a horizontally disposed cam 1.71 which is adapted to move the pins 153 vertically upward for the purpose of operatively positioning or throwing in the clutches 159a. This selector arm '170 is attached to a collar 172 disposed directly beneath the main gear 149 and secured to the upper end of a sleeve bearing 173, the latter journalled-in a bearing 174 on the gear housing. A bevel gear 175 or pinion at the lower end of the sleeve 173 meshes with a pinion 176 which in turn is provided with a sleeve 177 journaled in a bearing 178 on the lower side of the gear casing 140.

The sleeve 177 carried by said bevel gear 176 is provided with a longitudinal internal keyway 179 near its outer end. A key 180 at the inner end of a control shaft 181, is adapted at times to seat in said keyway and thereby provide means whereby rotation of the shaft will impart corresponding movement to the gear 176 and thence to the selector arm 170. 'I'his shaft 181 is journaled in a sleeve extension 182 on the `gear 152 and may be moved axially to thereby alternately make and break operative connection between said shaft and the gear 176. This control shaft 181 extends outwardly through the central column to a point at which an operating handle 183 may be conveniently attached thereto, said. handle or crank'lever including a sleeve 184 which telescopes over. and is separably secured to the outer end of said shaft. This sleeve is provided with a pointer 185 which cooperates with an indicator plate 186 in indicatingwhich of the cams has been selected for adjustment. Operative connection between the shaft 181 and the sleeve 182 which carries the gear 152 is obtained when desired by a simple clutch including a sleeve 187 attached to the shaft 181 and provided with recesses 188 designed to receive lingers 189 at the outer end of the sleeve extension 182. Thus, by moving the handle 183 inwardly, operative connection between the shaft 181' and gear 152 is obtained for adjusting a selected cam and connection between said shaft and the gear 176 of the selecting device is broken. Outward movement of the handle 183 to another operating position establishes ydriving connection between the shaft 181 and gear 176 for selecting acam and breaks connection between said shaft and the gear sri 152 of the adjusting device. Accordingly, it is understood that rotation of the handle 183 while in one position will select the cam mechanism to be adjusted and in another position adjusts the selected cam mechanism.

In order that rotation of the shaft 181 for the purpose of adjusting the selected cam mechanism will not, due to friction, change the setting of the selector arm 170, we have provided a locking device which is disposed between the bevel gears 152 and 176 (Figs. 6 and 8) and holds the latter against accidental rotation. This locking device consists of an annular series of recesses 190 provided at the outer end of the sleeve 177, said recesses corresponding in number to the number of cam mechanisms which are to be adjusted. These recesses 190 (Figs. 7 and 8) are arranged in diametrically opposed pairs and intended at times to be aligned with a pair of opposed notches 191 which are formed in and open through the outer end of a sleeve 192 on the bearing 178. Opposed locking fingers 193 on a collar 194 carried by the shaft 181 are adapted for projection into the aligned notches and recesses 190 and 191 when said shaft is moved to its innermost position. A lock ring 195 is pinned to the shaft 181 and serves to secure the collar 194 and ngers 193 thereon in a predetermined position on said shaft. By reference to Figs. 6, 7, and 8, it will be apparent that when these ngers 193 are projected into aligned pairs of the recesses 190, the gear 176 will thereby be securely held against rotation in the bearing 178.

By reference to Figs. 1, 3, 4, and 5, the operating connections between the selecting and adjusting devices and the various cam mechanisms will be understood. In providing operating connection between the selecting and adjusting devices as a unit and the adjustable cams referred to heretofore, substantially the construction now to be described is employed. The dip cam (Figs. 10 and 13-A) which controls the lowering of the blank molds into contact with the supply body of glass is connected to said devices through the shaft 64 which in turn is connected by gears to a shaft 64a. This shaft 64a (Figs. 1, 4, and 5) has driving connection to a vertical shaft 64b which extends vertically downward and is connected to one of the clutch operating pins 153. 'Ihe cam section (Figs. 10 and 13-A) for controlling lifting of the blank molds upon completion of the charging operation, is connected to the shaft 70. This shaft in turn is connected through meshing bevel gears to a horizontal shaft a which is suitably connected to a vertical shaft 7Gb, the lower end of the latter being suitably secured to the shaft 197 (Fig. 6).

The knife swinging or cut-off cam .121 (Fig. 22) is operatively connected to an adjusting shaft 131 which is connected through bevel gears to a shaft 131a. The inner end of this shaft 131a is suitably connected to the upper end of a vertical shaft 131b (Figs. 1, 3, 5 and 6). The knife drop cam 122 (Figs. 1 and 22) is connected through the meshing gears 132 and 133 and gears 133a to the upper end ofa vertical shaft 133b which extends downwardly to the selecting and adjusting devices.

The plunger lifting cam (Figs. 1 and 17) is connected to the selecting and adjusting devices through the shaft 120, the inner end of which is suitably connected to a vertical shaft E. This shaft is suitably connected to one of the vertical pins 153. The adjustable section 80 of the blank mold cam (Figs. 1, 19, and 19-A) is connected to the selecting and adjusting devices by means of the radial shaft 94, the inner end of which has driving connection through meshing bevel gears to a vertical shaft 94EL extending upwardly from the gear housing 140. Operative connection of the neck mold opening cam 79 (Fig. 14) to the selecting and adjusting devices, includes a shaft 109 and a second shaft 109a which extends partly across the interior of the stationary column 41 and has gear connection to the upper end of a shaft 1091. This shaft 109la is suitably connected to one of the vertical pins 153.

The timed relation between lifting of the blank molds and swinging of the cut-01T knives must be such that the blank molds will have assumed a predetermined elevation prior to swinging of the cut-off knives across the lower ends of the molds. It is obvious that improper setting of the cams controlling these operations might easily result in breaking of the molds and/or knives which would seriously affect operation of the machine. In order to avoid the possibility of such improper relative setting of these cams, automatic devices have been provided to limit the extent to which the cams controlling 'lifting' of the molds and 100 swinging of the cut-off knives may be adjusted relative to each other.

The construction whereby such control may be obtained is substantially as follows. A pinion 196 (Figs. 5 and 6) is secured to the vertical shaft 1 197 which extends upwardly from the selecting and adjusting devices to the blank mold lifting cam 66, said pinion running in mesh with a gear 198 having a sleeve extension 199 thereon journaled in a vertical bearing 200 above the gear l housing 140. This sleeve 199 is formed with internal screw threads throughout its length with which an externally threaded nut 201 is engaged. This nut 201 is splined to a vertical shaft 202 which extends axially through the bearing 200, 1 and is held against downward movement by a retaining collar 203 secured thereto just above the upper end of said bearing. This shaft 202 extends a short distance below the gear 198 where it is connected to a gear 204 running in 1 mesh with a pinion 205 secured to a shaft 206 which provides operating connection between the selecting and adjusting device and the cam which swings the cut-of knives inwardly across the lower end of the blank molds. l

By reference to Fig. 6 it will be noted that the nut 201 is in its lowermost position. It will be assumed that with the nut so positioned the blank mold lifting cam 66 and knife swinging cam 125, are adjusted as close together as possi- 1 ble and that any additional adjustment of one cam toward the other would result in seriously damaging both the cut-off knife and blank molds. If under these conditions, the operator should attempt to bring the cams closer together, the nut f 201 being incapable of further axial movement because of contact with the bushing 198a locks the adjusting mechanism so that the operating crank 1 83 cannot be moved to bring the blank mold lifting and cut-off cams closer together. However, by reversing the direction of rotation of the crank 183, the nut 201 will thread itself upward and simultaneously the cut-off cam 125 will be thereby adjusted away from the blank mold lifting cam 66, or vice versa, depending upon j, which cam is being adjusted. Then the other cam which was not adjusted can be moved closer to the first adjusted cam, causing the nut 201 to travel down again until the desired adjustment has been effected or the nut reached its lowermost 1 limit. Overlapping of these two operations is thereby positively avoided. In the event both the blank mold lifting and knife swinging operations are to be advanced and the time interval between lifting of the molds and the cutting stroke of the knives lengthened, it is obvious that the pinion 196 (Fig. 6) will be rotated to move the cam in a counter clockwise direction until the molds are being lifted at the desired point. Such rotation of the pinion 196 will operate through the gear 198 to move the nut 201 upwardly in the sleeve 199. The extent of this upward movement is, of course, dependent upon the degree of adjustment of the mold lifting cam. 'Ihe pinion 205 will now be rotated and operate through a shaft to move the knife swinging cam 125 (Fig. 22) in a counter clockwise direction. This adjustment results in rotation of the gear 204 (Fig. 6) and downward movement of the nut 201 in the sleeve 199. Here again the extent of downward movement of the nut 201 will be determined by the final spacing between the operating positions of the blank mold lifting and knife swinging cams.

In describing the manner in which the invention is operated We will assume that the machine is running at a normal speed and it is desired to retard the point at which the blank molds are lifted out of the supply body of glass preparatory to severing the gathered mold charges from said supply body. Without in anyway interfering with the normal speed of rotation of the mold carriage, the control handle 183 or lever is moved to its outermost position thereby moving the key 180 (Fig. 8) into the keyway 179 and operatively connecting the shaft 181 and bevel gear 176 and simultaneously breaking operative connection between said shaft and the bevel gear 152. The handle 183 is then rotated to bring the selector arm 170 to a position in which the cam 171 carried thereby raises a clutch pin 159 to thereby establish driving connection between the pinion 150 and pin 153 which are directly associated with the dip cam shaft 197. This completes -the cam selecting operation. 'I'he operating handle 183 may now be moved to its innermost position so that the locking fingers 193 (Figs. 6 and 8) are projected into the aligned recesses or notches 190 and 191. Thus the gear 176 is positively secured against rotation with the shaft 181. Upon completion of this locking operation and the establishment of driving connection between the shaft 181 and the gear 152, thehandle 183 is rotated with the result that rotary motion is im parted to the gear 149 and pinions 150 unless stop nut 201 is engaged with bushing 198B. Since only the pinion directly associated with the dip cam shaft 197 is operatively connected to its supporting pin 153, this cam alone will be adjusted. When the desired adjustment of the dip cam has been obtained, the control handle may again be moved 'to its outermost position and given a slight rotary motion to throw out the clutch pin 159. ,All of the pinions 150 lmay then be moved without affecting the setting of any of the cam mechanisms. This is particularly desirable in the event of accidental rotation of thesh'aft 181. Procedure similar to that just set forth is involved in adjusting any and all of the cam mechanisms described heretofore.

In Figs. 25, 26, and 27, we have illustrated another form of selecting and adjusting devices in which each of the cam mechanisms is provided v with an indicator whereby the operator may determine the exact position of any cam-and the extent to which it may be adjusted in either direction. Also a slightly modified form of driving connection between the operating handle 183 and gears 152 and 176 is disclosed in Figs. 25 and 27. The indicator construction consists of a bevel gear 207 on each of the vertical shafts which lead from the selecting and adjusting devices to the individual cams. Each bevel gear 207 meshes with a bevel pinion 208 which is connected through a flexible shaft 209 to a pinion 210 meshing with a bevel ring gear 211, the latter provided at one margin of an indicator drum 212 having graduations and numerals thereon, by means of which the operator may determine the limits of adjustment and particular setting of a given cam. These indicator drums 212 are mounted upon a shaft 213 enclosed in a housing 214 having a sight opening 215 through which the operator may view the numerals on the indicator drums. The control handle 183 carries a collar 216 which is slidingly supported on a shaft 217 extending through the central column, said shaft having its inner end connected to ,a bevel gear 176 forming part of the selecting device. The outer end of this collar 216 is formed with a notch 218 or recess, adapted to receive a finger 219 or lug, which is suitably fixed to the outer end of the shaft 217. By moving the collar voutwardly to interengage the finger 219 and 'recess 218, operative connection between the handle 183 and shaft 217 is established. Rotation of the handle while so positioned will result in movement of the selector arm 170 and cam 171 thereon as desired. The inner end of the collar 216 is provided with opposed notches 220 which at times engage fingers or lugs 221 at the outer end of a sleeve 222 which surrounds a portion of the shaft 217 and is connected at its inner end to a sleeve extension on the bevel gear 152, the latter designed to impart motion to the cam adjusting device. By moving the handle 183 inwardly to interengage the notches and recesses 220 and 221, and then rotating said handle, rotary motion will be transmitted through the sleeves 222 and 223 to said bevel gear- 152 and thence tothe adjusting means. An indicator 186 is provided for cooperation with a pointer 185 on the collar 216 as in the preceding form.

In Fig. 28 we have illustrated a modification in the cam selecting device and in this ligure and in Fig. 29, have shown an automatic means for locking the several adjustable cams against accidental movement. The selecting mechanism shown in Fig. 28 differs mainly from the mechanisms above described, in the substitution of a rotary cam and bell crank lever for the selector arm 170 shown in the preceding forms. The specific construction involved comprises a rotary selector cam 224 keyed to the main shaft 144 just above the gear 149. This cam is provided with ,a recess 225 in its periphery designed to receive rollers 226 on bell crank levers 227 which are individual to the adjustable cam mechanisms and serve to operatively and inoperatively position clutches 228. These levers 227 are pivoted to horizontal hinge pins 229 which are suitably attached to the closure plate on the upper side of the gear housing 140, said levers each including a pair of arms 230 and a movable clutch head 231.

gear housing 140 for connection to one of .the horizontal shafts directly associated with an adjustable cam. The other clutch head 233 is in the form of a notched sleeve extension on one of the pinions 150. A coil spring 234 is arranged This clutch head 231 is splined to a shaftv 232 which extends through the upper end of the above each movable clutch head 231 and exerts a downward pressure thereon tending to throw in the corresponding clutch. Rotation of the control handle 183 during a cam selecting operation imparts rotary motion to the selector cam 224 by way of the meshing bevel gears 235 and shafts 236 and 144. At the time the cam to be adjusted is selected, the corresponding bell crank lever 227 is rocked about its supporting hinge pin by means of one of the coil springs 234. After the cam has been selected and the control handle 183 moved as in the preceding form so that with rotation it will operate through the meshing gears 237 to rotate the gear 149 and pinions 150, a cam locking device which will now be set forth, is operated to release the cam for adjustment.

These holding devices are individual to the adjustable cams (Fig. 29) each including a rack bar 238, secured to the adjustable cam and corresponding in length to the range of adjustment of said cam. A lock bar 239 having a plurality of teeth 240 at its outer end which are to mesh with the teeth on the rack bar 238, is mounted in a stationary radial slideway 241. Levers 242 connect the lock bar 239 and a piston motor 243, said motor including a piston 244 directly connected through a. rod 245 to the levers 242. A coil spring 246 encircles the piston rod 245 and normally holds the pistons and levers in such 'position that the lock bar holds the corresponding cam against movement. When the cam is to be released from the influence of the locking device, air under pressure is supplied to the piston motor 243 by way of a pipe 247 to thereby counteract the effect of the coil spring 246 and through said piston lever retract the lock bar 239 from engagement with the rack bar 238. The application of air to the piston motors 243 is controlled in part by means which is autolmatically actuated by and simultaneously with selection of a cam for adjustment, and in part by a manually controlled valve as will now be described.

A circular air chamber 248 (Fig. 28) is arranged centrally above the gear housing 140 and communicates by way of valved ports 249 with an annular series of chambers 250 each of which is connected to one of the air pipes 247 leading to the piston motors 243. Valves 251 individual to the ports 249 and normally closed by springs 252 are provided with stems 253 projecting downwardly into the gear housing 140. These valve stems 253 are adapted to be raised one at a time for the purpose of opening the corresponding valve 251, by means of a radial finger 254 which is disposed directly above the notch 225 in the cam 224, said finger connected to the latter by a sleeve 255. Thus, positioning of the cam to permit rocking of one of the bell crank levers 227 automatically opens one of the spring pressed valves 251. Immediately upon opening one of the valves 251, a main control valve 256 maybe opened to permit the passage of air under pressure through the pipes 257 to the circular air chamber 248. This main valve 256 includes a rotary valve body 258 and a housing 259 therefor. An arcuate passageway .260 through the valve body 258 at times provides communication between the two pipes 257 and at other times establishes communication between an exhaust port 261 in the valve housing 259 and the pipe 257 which has direct connection with the circular air chamber 248.

In view of the above it will be understood that in operating the selectingl and adjusting devices shown in Figs. 28 and 29, the control handle 183 will be so positioned that rotation thereof will move the selector cam 224 to a position in which it will permit rocking of the bell crank lever corresponding to the cam to be adjusted. Here the bell crank lever will rock under influence of the corresponding coil spring 234. Also, the valve lifting iinger 254 will open the corresponding valve 251. This operation will be followed by opening of the main control -valve 256 so that air under pressure will be supplied to the circular air chamber 248 and thence by way of the port 249 to the individual chamber 250 corresponding to the cam to be adjusted. This air under pressure will then flow through one of the pipes 247 to one of the piston motors 243 with the result that the corresponding lock bar 239 is moved radially inward to an inoperative position. The main control handle 183 is then moved to a position in which rotation therof will operate through the meshing bevel gears 237 to rotate the several pinions 150 and through one of them the corresponding connecting shaft, adjust the cams as may be required.

In view of the foregoing it will be apparent that the present invention provides novel and exceptionally simple means for adjusting and controlling with unusual accuracy the various operations which` are performed upon mold charges of molten glass in transforming them into finished articles of hollow glassware.

Modications may be resorted to within the spirit and scope of the appended claims.

What We claim is:

l. In combinationan annular series of article forming units mounted for rotation about a vertical axis, means for rotating said units to thereby move them in succession past a series of operating positions, adjustable cams common to all of the units arranged at said positions, means providing operating connection between the cams and said units, adjusting devices individual to the cams and each operable without interrupting rotation of said units to adjust its associated cam with respect to the others, means for actuating said adjusting devices, and a selecting device operable to effect an operative connection between any selected adjusting device and said actuating means.

2. In combination, an annular series of article forming units mounted for rotation about a vertical axis, means for rotating said units to thereby move them in succession past a series of operating positions, adjustable cams common to all of the units arranged at said positions, means providing operating connection between the cams and said units, adjusting devices individual to the cams and each operable without interrupting rotation of said units to adjust its associated cam with respect to the others, means for actuating said adjusting devices, a selecting device operable to effect an operative connection between any selected adjusting device and said actuating means, and means operated by adjusting the cams to indicate the relative positions of the cams and the extent to which they may be adjusted.

3. In combination, a series of adjustable cams for operating mechanisms in a predetermined order, a series of shafts individual to the cams, means whereby rotation of the shafts adjusts the operating position of the cams, pinions individual to said shafts, a driving gear meshing with said pinions, clutches for providing driving connection between the pinions and corresponding shafts, means for operating the clutches one at a time to select the cam to be adjusted, and means for rotating said gear to thereby adjust the position of the selected cam.

4. In combination, a series of adjustable cams for operating mechanisms in a, predetermined order, a series of shafts individual to the cams, means whereby rotation of the shafts adjusts the operating position of the cams, pinions individual to said shafts, a driving gear meshing with said pinions, clutches for providing driving connection between the pinions and corresponding shafts, means for operating the clutches one at a time to select the cam to be adjusted, means for rotating said gear to thereby adjust the position of the selected cam, and means including meshing gears and pinions connecting at least one pair of said shafts to limit adjustment of one cam relative to another cam and thereby maintain a predetermined space relation between the operating positions of said cams.

5. In combination, a series of adjustable cams for operating mechanisms in a predetermined order, a series of shafts individual to the cams, means whereby rotation of the shafts adjusts the operating position of the cams, pinions individual to said shafts, a driving gear meshing with said pinions, clutches for providing driving connection between the pinions and corresponding shafts, a cam selecting device including means for throwing the clutches in and out one at a time, and means including a single operating handle for rotatingI the driving gear and actuating the clutch operating means.

6. In combination, a series of adjustable cams for operating mechanisms in a predetermined order, a series of shafts individual to the cams, means whereby rotation of the shafts adjusts the operating position of the cams, pinions indi-V vidual to said shafts, a driving gear meshing with said pinions, clutches for providing driving connection between the pinions and corresponding shafts, a cam selecting device including means for throwing the clutches in and out one at a time, means including a single operating handle for rotating the driving gear and actuating the clutch operating means, and a locking device common to said clutches for securing the clutches one at a time against disengagement during-adjustment of the corresponding cams.

7. In combination, a series of adjustable cams for operating a group of mechanisms in a predetermined order, manually controlled means for selecting and adjusting said cams one at a time, holding devices for securing the cams against accidental movement from their roperating positions, spring means normally operatively positioning the holding devices, and pneumatic means for inoperatively positioning said holding devices one at a time.

8. A cam selecting and adjusting mechanism comprising a driving gear, pinions meshing with said" gear, shafts individual to the pinions, clutches individual to the pinions and shafts and adapted to be positioned one at a time for operatively connecting pinions to corresponding shafts, manually controlled means for selecting and throwing into operation any one of the clutches independently of the others, cams individual to the shafts, means whereby rotation of the shafts adjusts the operating positions of the cams, and means for rotating said driving gear.

9. A cam selecting and adjusting mechanism comprising a driving gear, pinions meshing with said gear, shafts individual to the pinions, clutches individual to the pinions and shafts and adapted to be positioned one at a time for operatively connecting pinions to `corresponding shafts, a rotary selector cam adapted to be positioned beneath the pinions one at' a time and thereby throw in one of the clutches, adjustable cams individual to the shafts, means whereby rotation of the shafts adjusts the operating positions of the cams, and means for rotating said driving gear.

10. A cam selecting and adjusting mechanism comprising a driving gear, pinions meshing with said gear, shafts individual to the pinions, clutches individual to the pinions and shafts and adapted to be positioned one at a time for operatively connecting pinions vto corresponding shafts, a rotary selector cam adapted to be positioned beneath the pinions one .at a time and thereby throw in one of the clutches, adjustable cams indivdual to' the shafts, means whereby r0- tation of the shafts adjusts the operating positions of the cams, means for rotating said driving gear, and a locking device for holding the selector cam against accidental movement while in position to select a cam for adjustment.

l1. Cam selecting and adjusting mechanism comprising a driving gear, an annular series of pinions meshing with said gear, shafts individual to the pinions, clutches individual to said pinions and adapted to provide driving connection between the pinions and corresponding shafts one at a time, a cam adjustable about the axis of said gear and operable thereby to throw in the clutches one at a time, cams individual to the shafts, means whereby rotation of said shaftsadjusts the operating positions of the cams, and a single operating handle for selectively actuating the driving gear and clutch cam.

12. Camy selecting and adjusting means comprising-` shafts individual to cams to be adjusted, pinions individual to the shafts, clutches individual to the shafts and operable one at a time to provide driving connection between a pinion and a shaft, a driving gear meshing with said pinions, a drive shaft upon which said gear is supported, and manually controlled means for rotating said drive shaft.

13. Cam selecting and adjusting mechanism comprising a gear housing, a centrally disposed driving element,` a driving gear thereon, pinions running in mesh with said driving gear, shafts individual to cams to be adjusted, clutches adapted to provide operative connection between the said shafts and pinions, a selector cam for actu- 13() ating said clutches one at a time and thereby establishing driving connection between a shaft and pinion, and means for rotating said driving element.

14. Cam selecting and adjusting mechanism comprising a gear housing, a centrally disposedA driving element, a driving gear thereon, pinions running in mesh with said driving gear, shafts individual to cams tobe adjusted, clutches adapted to provide operative connection between the shafts and pinions, a selector cam for actuating said clutches one at a time and thereby establishing driving connection between a shaft and pinion, a sleeve surrounding a portion of said driving element and supporting said selector cam, and a single control device for rotating said driving element and sleeve one at a time.

15. Cam selecting and adjusting mechanism comprising a gear housing, a centrally disposed driving element, a driving gear thereon, pinions y 

